US20100296923A1 - Rotary machine scroll structure and rotary machine - Google Patents
Rotary machine scroll structure and rotary machine Download PDFInfo
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- US20100296923A1 US20100296923A1 US12/747,978 US74797809A US2010296923A1 US 20100296923 A1 US20100296923 A1 US 20100296923A1 US 74797809 A US74797809 A US 74797809A US 2010296923 A1 US2010296923 A1 US 2010296923A1
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- Prior art keywords
- casing
- scroll
- rotary machine
- rotational axis
- main body
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D9/00—Stators
- F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
- F01D9/026—Scrolls for radial machines or engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
- F01D25/243—Flange connections; Bolting arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2230/00—Manufacture
- F05D2230/60—Assembly methods
- F05D2230/64—Assembly methods using positioning or alignment devices for aligning or centring, e.g. pins
- F05D2230/642—Assembly methods using positioning or alignment devices for aligning or centring, e.g. pins using maintaining alignment while permitting differential dilatation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2250/00—Geometry
- F05D2250/40—Movement of components
- F05D2250/41—Movement of components with one degree of freedom
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2260/00—Function
- F05D2260/30—Retaining components in desired mutual position
Definitions
- the present invention relates to a rotary machine scroll structure used for a rotary machine such as a steam turbine and a gas turbine, as well as to the rotary machine.
- a scroll structure used for a rotary machine such as a turbine is disposed in front of a first stator blade (inflow side of working fluid) or behind a last rotor blade (outflow side of working fluid) in a turbine using heated steam or heated gas as the working fluid, and the scroll structure is a sheet metal welded structure through which the working fluid flows (see Patent document 1 for example).
- a conventional scroll structure includes an upper casing and a lower casing which are divided by a horizontal surface, and the upper casing and the lower casing are fastened to each other using a bolt (see Patent document 2 for example).
- the scroll structure has a heat shield effect with respect to a peripheral stationary member, and a rectifying effect for working fluid.
- the scroll structure When working fluid which flows into or out of a turbine is high temperature, the scroll structure shields radiant and heat transfer from the working fluid, and prevents rise in temperature of a member in the peripheral stationary member such as an inner casing.
- a material having high strength at a high temperature is selected as a material for the scroll structure. Further, in order to satisfy the material strength required to the scroll structure, an outer peripheral surface of the scroll structure is sprayed with cooling fluid to decrease the temperature of the scroll structure.
- a channel in front of a first stator blade or behind a last rotor blade in the scroll structure is formed into such a shape that aerodynamics are taken into consideration so as to rectify working fluid.
- a pressure loss of the working fluid is suppressed, and the performance of the turbine is improved.
- Patent document 1 Japanese Unexamined Patent Application, Publication No. H1-117929
- Patent document 2 Japanese Examined Patent Application, Publication No. S60-6607
- the scroll structure is divided into two pieces by the horizontal surface as described above, the upper casing and the lower casing are provided with connecting flanges. Thus, there is a problem that the scroll structure is increased in size.
- a shape of the channel in the scroll structure is not a shape in which aerodynamically loss is minimized, and there is problem that a pressure loss of working fluid is generated.
- the present invention has been accomplished to solve the above problems, and it is an object of the present invention to provide a rotary machine scroll structure and a rotary machine capable of improving reliability and performance of the rotary machine, and of reducing in size the rotary machine and the scroll structure.
- the present invention provided the following means.
- a rotary machine scroll structure includes: a casing that entirely covers an area surrounding an annular channel extending in a circular shape about a rotational axis in a rotating portion of the rotary machine and a cylindrical channel extending from the annular channel towards the rotational axis side and also extending towards the rotating portion; and a fitting portion that supports the casing with respect to a support portion accommodating the casing so as to enable expansion and contraction in a radial direction centered on the rotational axis.
- the casing is integrally formed in one piece, a working fluid is prevented from leaking outside, and another fluid is prevented from flowing into the casing from outside which may be caused by inhalation of the other fluid. That is, in a case where the casing is divided into two pieces, i.e., into the upper casing and the lower casing, there is an adverse possibility that the working fluid leaks from the joint surface between the upper casing and the lower casing. In the case of the integrally formed casing, however, since there is no joint surface, it is possible to reliably prevent the working fluid from leaking.
- the cylindrical channel can be formed into such a shape that a pressure loss thereof is suppressed as compared with a case where the casing is divided into two pieces. That is, when the casing is divided into two pieces, a space for disposing a member such as a bolt which fastens the upper casing and the lower casing and a space where the bolt is attached or detached must be secured, so that the shape of the cylindrical channel is limited. To the contrary, in the case of the integrally formed casing, it is unnecessary to use the fastening bolt. Therefore, the shape of the channel is not limited, and a channel shape having a small pressure loss can be employed.
- the scroll structure can be reduced in size as compared with the case where the casing is divided into two pieces. That is, when the casing is divided into two pieces, flanges used for fastening the upper casing and the lower casing to each other project outward from the casings. On the other hand, when the casing is integrally formed in one piece, it is unnecessary to provide the flanges. Therefore, the casing can be reduced in size.
- Thermal deformation of the casing is not restrained, and misalignment and thermal stress of the casing can be suppressed.
- the rotary machines include general fluid machines such as a steam turbine, a compressor, and a pump.
- the fitting portion includes: a first protrusion disposed on one of the casing and the support portion and protruding in one direction along the radial direction; a first groove which is disposed on the other one of the casing and the support portion, which is open towards another direction along the radial direction, which extends in a circumferential direction of the rotational axis, and into which the first protrusion is fitted; and a first depression which is formed by indenting one wall constituting the groove is depressed in one direction along the radial direction and through which the first protrusion passes by moving relative to the one wall in a direction along the rotational axis.
- the casing is supported such that it can expand and contract along the radial direction, and movement of the casing in the direction extending along the rotational axis is restricted.
- the first protrusion projecting in one of the directions along the radial direction is opened in the other direction along the radial direction, and the first protrusion is fitted into the first groove extending in the circumferential direction.
- relative movement between the first protrusion and the first groove along the rotational axis is restricted.
- relative movement between the first protrusion and the first groove in the radial direction is permitted.
- the casing can be supported such that it can expand and contract along the radial direction and movement of the casing in the direction along the rotational axis can be restricted.
- the first protrusion is disposed in the first groove by moving the first protrusion in the direction along the rotational axis to pass through the first depression, and the rotation shaft of the rotary machine penetrates the casing. Thereafter, the first protrusion is rotated in the circumferential direction, and the first protrusion is disposed in a region of the first groove where the first depression is not provided, in other words, a region where a pair of walls are opposed to each other. Accordingly, relative movement between the first protrusion and the first groove along the direction of the rotational axis is restricted.
- the fitting portion includes: a second protrusion which is disposed on one of the casing and the support portion and which protrudes in one direction along the radial direction; and a second depression which is disposed on the other one of the casing and the support portion, which is open towards another direction along the radial direction, and into which the second protrusion is fitted.
- the casing is supported such that it can expand and contract in the radial direction, and movement of the casing in the direction intersecting with the rotational axis is restricted.
- the second protrusion which projects in one direction along the radial direction is fitted into the second depression which is depressed in the one direction along the radial direction.
- relative movement between the second protrusion and the second depression in the direction intersecting with the rotational axis is restricted.
- relative movement between the second protrusion and the second depression in the radial direction is permitted.
- a rotary machine in a second aspect of the present invention, includes: a scroll structure according to the first aspect; and a rotating portion into which or from which a working fluid flows, between the rotating portion and the scroll structure, and which extracts a rotational driving force from the supplied working fluid.
- the rotary machine since the rotary machine includes the scroll structure of the first aspect, leak of the working fluid which flows into or from the rotating portion can reliably be prevented, and reliability of the rotary machine is improved.
- the rotary machine includes the scroll structure of the first aspect, a pressure loss of the working fluid which flows into or from the rotating portion can be reduced, and performance of the rotary machine is improved.
- the rotary machine includes the scroll structure of the first aspect, the casing is reduced in size, and the rotary machine is thus reduced in size.
- FIG. 1 is a schematic diagram for describing an entire configuration of a gas turbine according to an embodiment of the present invention.
- FIG. 2 is a perspective view for describing a configuration of an inlet scroll portion shown in FIG. 1 as viewed from the turbine portion.
- FIG. 3 is a perspective view for describing the configuration of the inlet scroll portion shown in FIG. 1 as viewed from a casing.
- FIG. 4 is a partial enlarged sectional view for describing a configuration of a turbine portion-side restraining portion and a casing-side restraining portion shown in FIGS. 2 and 3 .
- FIG. 5 is a partial enlarged view for describing a configuration of the turbine-side restraining portion shown in FIG. 4 .
- FIG. 6 is a partial enlarged view for describing the configuration of the turbine-side restraining portion shown in FIG. 4 .
- FIG. 7 is a sectional view for describing a disposition of a horizontal restraining portion and a vertical restraining portion shown in FIG. 2 .
- FIG. 8 is a partial enlarged view for describing a configuration of the horizontal restraining portion shown in FIG. 7 .
- FIG. 9 is a sectional view for describing the configuration of the horizontal restraining portion shown in FIG. 7 taken along line A-A.
- FIG. 10 is a partial enlarged view for describing a configuration of the vertical restraining portion shown in FIG. 7 .
- FIGS. 1 to 10 A scroll structure according to an embodiment of the present invention and a gas turbine having the scroll structure will be described with reference to FIGS. 1 to 10 .
- FIG. 1 is a schematic diagram for describing an entire configuration of the gas turbine according to the present embodiment.
- a gas turbine (rotary machine) 1 includes casings (support portions) 2 A, 2 B and 2 C constituting an outer shape of the gas turbine 1 , a turbine portion (rotating portion) 3 which extracts a rotational driving force from a supplied working fluid, a rotation shaft 4 which is rotated and driven around a rotational axis L by the turbine portion 3 , an inlet scroll portion (scroll structure) 5 which supplies the working fluid to the turbine portion 3 , and a discharge scroll portion (scroll structure) 6 into which the working fluid discharged from the turbine portion 3 flows.
- the casings 2 A and 2 C constitute the outer shape of the gas turbine 1 together with the casing 2 B.
- the turbine portion 3 , the rotation shaft 4 , the inlet scroll portion 5 and the discharge scroll portion 6 are accommodated in the casings 2 A and 2 C.
- the casings 2 A and 2 C are substantially cylindrical members of which one ends are closed. In other words, the casings 2 A and 2 C are bottomed cylindrical members, so-called pot-like members. Open ends of the casings 2 A and 2 C are butted against each other, and are fastened to each other with the casing 2 B interposed therebetween.
- a through hole 7 is formed in the closed ends of the casings 2 A and 2 C, and the rotation shaft 4 is inserted through the through hole 7 .
- An opening 8 is formed in cylindrical surfaces of the casings 2 A and 2 C, and a tube through which the working fluid flows in or out is inserted through the opening 8 .
- the casing 2 B constitutes the outer shape of the gas turbine 1 together with the casings 2 A and 2 C, and supports the turbine portion 3 .
- the casing 2 B is a substantially disk-like member extending in a radial direction centered on the rotational axis L, and is interposed between the casings 2 A and 2 C.
- the turbine portion 3 includes a rotor blade 11 and a stator blade 12 (see FIG. 4 ).
- the turbine portion 3 extracts a rotational driving force from the working fluid supplied from the inlet scroll portion 5 , and rotates and drives the rotation shaft 4 .
- a known configuration can be used for the turbine portion 3 , and the configuration thereof is not especially limited.
- the rotation shaft 4 is rotated and driven around the rotational axis L by the turbine portion 3 as shown in FIG. 1 .
- the working fluid passes through the inlet scroll portion 5 and the discharge scroll portion 6 , and the working fluid is supplied to the turbine portion 3 as well as the working fluid discharged from the turbine portion 3 flows into the inlet scroll portion 5 and the discharge scroll portion 6 . Since the basic configurations of the inlet scroll portion 5 and the discharge scroll portion 6 are substantially the same, only the inlet scroll portion 5 will be described below and description of the configuration of the discharge scroll portion 6 is omitted.
- FIG. 2 is a perspective view for describing the configuration of the inlet scroll portion shown in FIG. 1 as viewed from the turbine portion.
- FIG. 3 is a perspective view for describing the configuration of the inlet scroll portion shown in FIG. 1 as viewed from the casing.
- the inlet scroll portion 5 includes a scroll main body (casing) 21 constituting the outer shape of the inlet scroll portion 5 , a turbine portion-side restraining portion (fitting portion) 22 A, a casing-side restraining portion (fitting portion) 22 B, a horizontal restraining portion (fitting portion) 23 A, and a vertical restraining portion (fitting portion) 23 B.
- These restraining portions support the scroll main body 21 with respect to the casing 2 A such that the scroll can expand and contract along the radial direction centered on the rotational axis L, and restrain movement of the scroll main body 21 in a direction along the rotational axis L.
- the scroll main body 21 is integrally formed into a ring shape provided at a central portion with an opening through which the rotation shaft 4 is inserted. As shown in FIG. 1 , the scroll main body 21 is provided therein with an annular channel 31 extending annularly around the rotational axis L, and a cylindrical channel 32 extending from the annular channel 31 toward the rotational axis L up to the turbine portion 3 .
- FIG. 4 is a partial enlarged sectional view for describing configurations of the turbine portion-side restraining portion and the casing-side restraining portion shown in FIGS. 2 and 3 .
- the turbine portion-side restraining portion 22 A is provided in the scroll main body 21 on the side of the turbine portion 3 .
- the turbine portion-side restraining portion 22 A supports the scroll main body 21 such that the scroll main body 21 can expand and contract in the radial direction centered on the rotational axis L, and restrains movement of the scroll main body 21 in the direction along the rotational axis L.
- the casing-side restraining portion 22 B is provided in the scroll main body 21 on the side of the casing 2 A.
- the casing-side restraining portion 22 B supports the scroll main body 21 such that the scroll main body 21 can expand and contract in the radial direction centered on the rotational axis L and restrains movement of the scroll main body 21 in the direction along the rotational axis L.
- the annular channel 31 has an annular shape into which the working fluid heated from outside flows.
- a cross sectional area of the channel is gradually reduced from a lower portion (lower portion in FIG. 1 ) to an upper portion along which the working fluid flows from outside.
- the cylindrical channel 32 extends from an inner periphery of the annular channel 31 toward the rotational axis L as well as extends toward the turbine portion 3 .
- the cylindrical channel 32 has such a shape that a pressure loss of the working fluid flowing through the cylindrical channel 32 is minimized.
- FIGS. 5 and 6 are partial enlarged views for describing a configuration of the turbine-side restraining portion shown in FIG. 4 .
- the turbine portion-side restraining portion 22 A supports the scroll main body 21 such that it can expand and contract in the radial direction, and restrains movement of the scroll main body 21 in the direction along the rotational axis L.
- the turbine portion-side restraining portion 22 A is provided with an outer ring 41 A which is disposed on an inner peripheral surface of the scroll main body 21 , and with an inner ring 42 A fixed to a support portion 35 which is connected to the casing 2 A.
- the outer ring 41 A is provided with first protrusions 43 A which project radially inward and which are disposed at equal distances from one another in the circumferential direction.
- the distances of the first protrusions 43 A correspond to the distances of later-described first depressions 45 A.
- the first protrusions 43 A are fitted into later-described first grooves 44 A, thereby restraining movements of the scroll main body 21 in the direction along the rotational axis L.
- the inner ring 42 A is provided with first grooves 44 A which are opened radially outward and extend in the circumferential direction, and first depressions 45 A which are formed in a wall portion 46 A of a pair of wall portions located on the side of the scroll main body 21 , and which are depressed radially inward.
- the pair of wall portions constitute the first groove 44 A.
- the first grooves 44 A are fitted to the first protrusions 43 A, restrain movement of the scroll main body 21 in the direction along the rotational axis L, and permit movement of the first protrusions 43 A in the circumferential direction.
- first protrusions 43 A When the first protrusions 43 A are fitted to or separated from the first grooves 44 A, the first protrusions 43 A move in the direction along the rotational axis L and pass through the first depressions 45 A.
- the first depressions 45 A are provided as many as the first protrusions 43 A at equal distances from one another in the circumferential direction. The distances between the first depressions 45 A correspond to the distances between the first protrusions 43 A.
- the first protrusions 43 A can pass through the first depressions 45 A and move in the direction along the rotational axis L.
- the relative position between the outer ring 41 A and the inner ring 42 A shown in FIG. 5 shows a positional relation in a case where the first protrusions 43 A pass through the first depressions 45 A.
- the relative position between the outer ring 41 A and the inner ring 42 A shown in FIG. 6 shows a positional relation in a case where the first protrusions 43 A rotate in the circumferential direction and restrain movement of the scroll main body 21 in the direction along the rotational axis L.
- the casing-side restraining portion 22 B supports the scroll main body 21 such that it can expand and contract in the radial direction and restrains movement of the scroll main body 21 in the direction along the rotational axis L.
- the casing-side restraining portion 22 B is provided with an outer ring 41 B which is disposed on a surface of the scroll main body 21 opposed to the casing 2 A, and with an inner ring 42 B fixed to the support portion 35 which is connected to the casing 2 A.
- the outer ring 41 B is provided with first protrusions 43 B which project radially inward and which are disposed at equal distances from one another in the circumferential direction.
- the inner ring 42 B is provided with a first groove 44 B which opens radially outward and which extends in the circumferential direction, and with a first depression 45 B which is depressed radially inward and which is formed in a first wall portion 46 B of a pair of wall portions constituting the first groove 44 B on the side of the scroll main body 21 .
- FIG. 7 is a sectional view for describing positions of the horizontal restraining portion and the vertical restraining portion shown in FIG. 2 .
- the horizontal restraining portion 23 A and the vertical restraining portion 23 B support the scroll main body 21 such that it can expand and contract in the radial direction, and restrain movement of the scroll main body 21 in the horizontal direction intersecting with the rotational axis L as well as in the vertical direction.
- the horizontal restraining portion 23 A is disposed on an upper end (upper side end in FIG. 7 ) of the scroll main body 21 , and restrains movement of the scroll main body 21 in the horizontal direction (lateral direction in FIG. 7 ) with respect to the casing 2 A.
- FIG. 8 is a partial enlarged view for describing a configuration of the horizontal restraining portion shown in FIG. 7 .
- FIG. 9 is a sectional view for describing the configuration of the horizontal restraining portion shown in FIG. 7 taken along the line A-A.
- the horizontal restraining portion 23 A is provided with a second protrusion 51 A projecting radially inward from the casing 2 A, and a pedestal 53 A formed with a second depression 52 A which is opened radially outward.
- the second protrusion 51 A includes a brim 61 A which abuts against an outer peripheral surface of the casing 2 A, a shaft portion 62 A which extends radially inward from the brim 61 A and which penetrates the casing 2 A, and an inserted portion 63 A which configures a radially inner end of the shaft portion 62 A and which is inserted into the second depression 52 A.
- the inserted portion 63 A has a rectangular cross section.
- the pedestal 53 A is a rectangular parallelepiped member provided on the scroll main body 21 .
- a rib 64 extending radially outward and in the circumferential direction is provided on a side surface of the pedestal 53 A.
- the second depression 52 A is provided on an upper surface of the pedestal 53 A, i.e., the surface of the pedestal 53 A opposed to the casing 2 A.
- the second depression 52 A is a rectangular parallelepiped hole, and the inserted portion 63 A is inserted into the second depression 52 A.
- the vertical restraining portion 23 B is disposed diagonally below the scroll main body 21 , e.g., at a phase rotated downward by about 20° from the horizontal direction, and the vertical restraining portion 23 B restrains movement of the scroll main body 21 in the vertical direction (vertical direction in FIG. 7 ) with respect to the casing 2 A.
- the phase is not limited to 20° as long as movement in the vertical direction is restrained.
- FIG. 10 is a partial enlarged view for describing the configuration of the vertical restraining portion shown in FIG. 7 .
- the vertical restraining portion 23 B includes a second protrusion 51 B projecting radially inward from the casing 2 A, and a pedestal 53 B formed with a second depression 52 B which is opened radially outward.
- FIG. 10 shows the configuration of the vertical restraining portion 23 B and description thereof is omitted.
- the working fluid which is heated to high temperature in a high temperature gas furnace flows into the inlet scroll portion 5 of the gas turbine 1 .
- the working fluid which has flowed into the inlet scroll portion 5 flows into the annular channel 31 , and then flows into the cylindrical channel 32 at a substantially even flow velocity in the circumferential direction.
- the working fluid which flowed into the cylindrical channel 32 is introduced into the turbine portion 3 and flows into the turbine portion 3 .
- the rotor blade 11 is rotated and driven by the working fluid flowing in the turbine portion 3 , and a rotational driving force extracted by the rotor blade 11 is transmitted to the rotation shaft 4 .
- the working fluid of which rotational driving force has been extracted by the turbine portion 3 and of which temperature has been lowered is discharged from the turbine portion 3 .
- the working fluid discharged from the turbine portion 3 flows into the cylindrical channel 32 of the discharge scroll portion 6 and flows toward the annular channel 31 .
- the working fluid which has flowed into the annular channel 31 is discharged from the discharge scroll portion 6 , i.e., from the gas turbine 1 , and is again introduced into the high temperature gas furnace through a device.
- the first protrusions 43 A and 43 B are disposed respectively in the first grooves 44 A and 44 B.
- the first protrusions 43 A and 43 B are disposed at positions where they are overlapped with the wall portions 46 A and 46 B as viewed from the direction along the rotational axis L.
- first protrusions 43 A and 43 B By disposing the first protrusions 43 A and 43 B at such positions, movement of the scroll main body 21 in the direction along the rotational axis L is restrained. By providing distances between inner peripheral ends of the first protrusions 43 A and 43 B and bottom surfaces of the first grooves 44 A and 44 B, the first protrusions 43 A and 43 B can move in the radial direction with respect to the first grooves 44 A and 44 B.
- the inner ring 42 A of the turbine portion-side restraining portion 22 A is fixed to the support portion 35 . Thereafter, the scroll main body 21 is fitted to the support portion 35 through the turbine portion-side restraining portion 22 A.
- first protrusion 43 A and the first depression 45 A are disposed at the relative positions shown in FIG. 5 , in other words, such that the first protrusion 43 A is inserted through the first depression 45 A and then, the scroll main body 21 is moved toward the turbine portion 3 along the rotational axis L.
- the first protrusion 43 A is moved into the first groove 44 A, the first protrusion 43 A is moved in the circumferential direction, and the first protrusion 43 A is rotated to a location where it is overlapped with the wall portion 46 A as viewed from the direction along the rotational axis L as shown in FIG. 6 . Accordingly, fitting operation of the turbine portion-side restraining portion 22 A is completed.
- the rotation shaft 4 is inserted through the integrally formed scroll main body 21 as well as the scroll main body 21 is supported such that it can expand and contract along the radial direction.
- movement of the scroll main body 21 in the direction along the rotational axis L can be restrained.
- the first protrusion 43 A passes through the first depression 45 A while moving the first protrusion 43 A in the direction along the rotational axis L. Accordingly, the first protrusion 43 A is disposed in the first groove 44 A and the rotation shaft 4 penetrates the scroll main body 21 . Thereafter, the first protrusion 43 A is rotated in the circumferential direction, and the first protrusion 43 A is disposed in a region of the first groove 44 A where the first depression 45 A is not provided, in other words, in a region of the first groove 44 A where the pair of wall portions are opposed to each other. Thus, movement of the scroll main body 21 in the direction along the rotational axis L is restrained.
- first protrusion 43 B and the first depression 45 B are disposed at the relative positions shown in FIG. 5 , and then the inner ring 42 B is moved toward the turbine portion 3 along the rotational axis L.
- the inner ring 42 B is moved in the circumferential direction, and the inner ring 42 B is rotated to a location where the first protrusion 43 B and the wall portion 46 B are overlapped with each other as viewed from the direction along the rotational axis L as shown in FIG. 6 . Accordingly, fitting operation of the casing-side restraining portion 22 B is completed.
- the second protrusion 51 A of the horizontal restraining portion 23 A is inserted into the second depression 52 A. Then, movement of the scroll main body 21 in the horizontal direction is restrained. A gap is provided between an inner radial end of the second protrusion 51 A and the bottom surface of the second depression 52 A, so that expansion and contraction of the scroll main body 21 in the radial direction are permitted.
- the scroll main body 21 by integrally forming the scroll main body 21 , leakage of the working fluid outside as well as inflow of other fluid caused by inhalation of the other fluid into the scroll main body 21 from outside can be prevented. That is, when the scroll main body 21 has such a configuration that it is divided into two pieces, i.e., the upper casing and the lower casing, there is an adverse possibility that a working fluid may leak from the joint surface between the upper casing and the lower casing. In the case of the integrally formed scroll main body 21 , since there is no joint surface, leakage of a working fluid can surely be prevented, and reliability of the gas turbine 1 can be improved.
- the cylindrical channel 32 can be formed into such a shape that a pressure loss thereof is suppressed. That is, when the scroll main body 21 is divided into two pieces, since a space for disposing a member such as a bolt which fastens the upper casing and the lower casing to each other and an space for operating attachment or detachment of the bolt must be secured, the shape of the cylindrical channel 32 is limited. To the contrary, in the case where the scroll main body 21 is integrally formed in one piece, it is unnecessary to use the fastening bolt, the shape of the channel is not limited, and thus the channel shape causing a small pressure loss can be employed. Therefore, performance of the gas turbine 1 can be improved.
- the scroll structure can be reduced in size.
- the flanges used for fastening the upper casing and the lower casing to each other project outward from the casings.
- the scroll main body 21 since it is unnecessary to provide the flanges, the scroll main body 21 can be made smaller, and the gas turbine 1 can be reduced in size.
- the scroll main body 21 is supported by the turbine portion-side restraining portion 22 A, the casing-side restraining portion 22 B, the horizontal restraining portion 23 A and the vertical restraining portion 23 B such that the scroll main body 21 can expand and contract in the radial direction. Therefore, it is possible to prevent misalignment of the scroll main body 21 which may be caused in a case where deformation of the scroll main body 21 is restrained, and damage to the scroll main body 21 caused by high stress.
- misalignment of the scroll main body 21 may be caused by uneven deformation.
- the fixed point there is an adverse possibility that thermal deformation of the scroll main body 21 is restrained and thermal stress is caused, and thus the scroll main body 21 is damaged.
- the present invention is applied to the axial-flow turbine in the above embodiment, the present invention is not limited to such an axial-flow turbine, but can also be applied to other kinds of turbines such as a centrifugal type turbine and a mixed-flow turbine.
- the present invention can also be applied to general fluid machines such as a gas turbine of another type in which air is employed as a working fluid and combustion energy of fossil fuel or the like is used as a heat source, as well as a steam turbine, a compressor, and a pump. Applications of the present invention are not especially limited.
Abstract
Description
- The present invention relates to a rotary machine scroll structure used for a rotary machine such as a steam turbine and a gas turbine, as well as to the rotary machine.
- Generally, a scroll structure used for a rotary machine such as a turbine is disposed in front of a first stator blade (inflow side of working fluid) or behind a last rotor blade (outflow side of working fluid) in a turbine using heated steam or heated gas as the working fluid, and the scroll structure is a sheet metal welded structure through which the working fluid flows (see
Patent document 1 for example). - A conventional scroll structure includes an upper casing and a lower casing which are divided by a horizontal surface, and the upper casing and the lower casing are fastened to each other using a bolt (see Patent document 2 for example).
- The scroll structure has a heat shield effect with respect to a peripheral stationary member, and a rectifying effect for working fluid.
- When working fluid which flows into or out of a turbine is high temperature, the scroll structure shields radiant and heat transfer from the working fluid, and prevents rise in temperature of a member in the peripheral stationary member such as an inner casing.
- In this case, a material having high strength at a high temperature is selected as a material for the scroll structure. Further, in order to satisfy the material strength required to the scroll structure, an outer peripheral surface of the scroll structure is sprayed with cooling fluid to decrease the temperature of the scroll structure.
- A channel in front of a first stator blade or behind a last rotor blade in the scroll structure is formed into such a shape that aerodynamics are taken into consideration so as to rectify working fluid. In this configuration, a pressure loss of the working fluid is suppressed, and the performance of the turbine is improved.
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Patent document 1 Japanese Unexamined Patent Application, Publication No. H1-117929
Patent document 2 Japanese Examined Patent Application, Publication No. S60-6607 - In a case where the scroll structure is divided into two pieces by the horizontal surface as described above, the upper casing and the lower casing are provided with connecting flanges. Thus, there is a problem that the scroll structure is increased in size.
- When the scroll structure is increased in size, a stationary part or the like which is disposed on an outer peripheral of the scroll structure such as an inner casing is also increased in size, and there are problems that the weight of the turbine is increased and cost for the materials is increased.
- In a case where there is a difference in pressure between an inside and an outside of the scroll structure, there are problems that working fluid leaks from a joint surface between the upper casing and the lower casing, fluid outside the scroll structure, e.g., air is inhaled from the joint surface and the fluid flows into the turbine and therefore the performance of the turbine is influenced.
- Further, in a structure in which the upper casing and the lower casing are fastened to each other using a bolt, it is necessary to secure an operation space where the scroll structure is assembled or disassembled, and the shape of the channel in the scroll structure is limited. In other words, a complicated shape in which aerodynamics are taken into consideration and a shape in which the scroll structure can be assembled or disassembled are not compatible with each other in terms of the structure.
- In the conventional scroll structure, higher priority is given to the shape in which the scroll structure can be assembled or disassembled, and as a result, a shape of the channel in the scroll structure is not a shape in which aerodynamically loss is minimized, and there is problem that a pressure loss of working fluid is generated.
- The present invention has been accomplished to solve the above problems, and it is an object of the present invention to provide a rotary machine scroll structure and a rotary machine capable of improving reliability and performance of the rotary machine, and of reducing in size the rotary machine and the scroll structure.
- In order to achieve the above objects, the present invention provided the following means.
- According to a first aspect of the present invention, a rotary machine scroll structure includes: a casing that entirely covers an area surrounding an annular channel extending in a circular shape about a rotational axis in a rotating portion of the rotary machine and a cylindrical channel extending from the annular channel towards the rotational axis side and also extending towards the rotating portion; and a fitting portion that supports the casing with respect to a support portion accommodating the casing so as to enable expansion and contraction in a radial direction centered on the rotational axis.
- According to the above aspect, since the casing is integrally formed in one piece, a working fluid is prevented from leaking outside, and another fluid is prevented from flowing into the casing from outside which may be caused by inhalation of the other fluid. That is, in a case where the casing is divided into two pieces, i.e., into the upper casing and the lower casing, there is an adverse possibility that the working fluid leaks from the joint surface between the upper casing and the lower casing. In the case of the integrally formed casing, however, since there is no joint surface, it is possible to reliably prevent the working fluid from leaking.
- When the casing is integrally formed in one piece, the cylindrical channel can be formed into such a shape that a pressure loss thereof is suppressed as compared with a case where the casing is divided into two pieces. That is, when the casing is divided into two pieces, a space for disposing a member such as a bolt which fastens the upper casing and the lower casing and a space where the bolt is attached or detached must be secured, so that the shape of the cylindrical channel is limited. To the contrary, in the case of the integrally formed casing, it is unnecessary to use the fastening bolt. Therefore, the shape of the channel is not limited, and a channel shape having a small pressure loss can be employed.
- By the casing integrally formed in one piece, the scroll structure can be reduced in size as compared with the case where the casing is divided into two pieces. That is, when the casing is divided into two pieces, flanges used for fastening the upper casing and the lower casing to each other project outward from the casings. On the other hand, when the casing is integrally formed in one piece, it is unnecessary to provide the flanges. Therefore, the casing can be reduced in size.
- As the casing is supported by the fitting portion such that the casing can expand and contract along the radial direction, misalignment of the casing caused by restraining deformation of the casing can be prevented, and damage to the casing caused by high stress can be prevented.
- For example, in a case where even a single fixed point is provided to the casing, misalignment of the casing may be caused by uneven deformation. When the fixed point is provided, there is an adverse possibility that thermal deformation of the casing is restrained to cause thermal stress, and the casing is damaged.
- When the casing is supported such that the casing can expand and contract along the radial direction, distortion of the shape of the casing is suppressed, and the working fluid is prevented from leaking from a connected portion with another member.
- Thermal deformation of the casing is not restrained, and misalignment and thermal stress of the casing can be suppressed. Examples of the rotary machines include general fluid machines such as a steam turbine, a compressor, and a pump.
- In the above aspect, it is preferable that the fitting portion includes: a first protrusion disposed on one of the casing and the support portion and protruding in one direction along the radial direction; a first groove which is disposed on the other one of the casing and the support portion, which is open towards another direction along the radial direction, which extends in a circumferential direction of the rotational axis, and into which the first protrusion is fitted; and a first depression which is formed by indenting one wall constituting the groove is depressed in one direction along the radial direction and through which the first protrusion passes by moving relative to the one wall in a direction along the rotational axis.
- According to the above aspect, the casing is supported such that it can expand and contract along the radial direction, and movement of the casing in the direction extending along the rotational axis is restricted.
- Specifically, the first protrusion projecting in one of the directions along the radial direction is opened in the other direction along the radial direction, and the first protrusion is fitted into the first groove extending in the circumferential direction. In this configuration, relative movement between the first protrusion and the first groove along the rotational axis is restricted. On the other hand, relative movement between the first protrusion and the first groove in the radial direction is permitted.
- Even when the rotation shaft of the rotary machine penetrates the casing, the casing can be supported such that it can expand and contract along the radial direction and movement of the casing in the direction along the rotational axis can be restricted.
- More specifically, the first protrusion is disposed in the first groove by moving the first protrusion in the direction along the rotational axis to pass through the first depression, and the rotation shaft of the rotary machine penetrates the casing. Thereafter, the first protrusion is rotated in the circumferential direction, and the first protrusion is disposed in a region of the first groove where the first depression is not provided, in other words, a region where a pair of walls are opposed to each other. Accordingly, relative movement between the first protrusion and the first groove along the direction of the rotational axis is restricted.
- In the above embodiment, it is preferable that the fitting portion includes: a second protrusion which is disposed on one of the casing and the support portion and which protrudes in one direction along the radial direction; and a second depression which is disposed on the other one of the casing and the support portion, which is open towards another direction along the radial direction, and into which the second protrusion is fitted.
- According to the above aspect, the casing is supported such that it can expand and contract in the radial direction, and movement of the casing in the direction intersecting with the rotational axis is restricted.
- Specifically, the second protrusion which projects in one direction along the radial direction is fitted into the second depression which is depressed in the one direction along the radial direction. In this configuration, relative movement between the second protrusion and the second depression in the direction intersecting with the rotational axis is restricted. On the other hand, relative movement between the second protrusion and the second depression in the radial direction is permitted.
- In a second aspect of the present invention, a rotary machine includes: a scroll structure according to the first aspect; and a rotating portion into which or from which a working fluid flows, between the rotating portion and the scroll structure, and which extracts a rotational driving force from the supplied working fluid.
- According to the above aspect, since the rotary machine includes the scroll structure of the first aspect, leak of the working fluid which flows into or from the rotating portion can reliably be prevented, and reliability of the rotary machine is improved.
- Since the rotary machine includes the scroll structure of the first aspect, a pressure loss of the working fluid which flows into or from the rotating portion can be reduced, and performance of the rotary machine is improved.
- Since the rotary machine includes the scroll structure of the first aspect, the casing is reduced in size, and the rotary machine is thus reduced in size.
- In the rotary machine scroll structure and the rotary machine according to the present invention, since the casing is integrally formed in one piece, there are effects that reliability and performance of the rotary machine are improved and the rotary machine and the scroll structure can be reduced in size.
- Further, since the casing is supported by the fitting portion such that the casing can expand and contract along the radial direction, there is an effect that reliability and performance of the rotary machine can be improved.
-
FIG. 1 is a schematic diagram for describing an entire configuration of a gas turbine according to an embodiment of the present invention. -
FIG. 2 is a perspective view for describing a configuration of an inlet scroll portion shown inFIG. 1 as viewed from the turbine portion. -
FIG. 3 is a perspective view for describing the configuration of the inlet scroll portion shown inFIG. 1 as viewed from a casing. -
FIG. 4 is a partial enlarged sectional view for describing a configuration of a turbine portion-side restraining portion and a casing-side restraining portion shown inFIGS. 2 and 3 . -
FIG. 5 is a partial enlarged view for describing a configuration of the turbine-side restraining portion shown inFIG. 4 . -
FIG. 6 is a partial enlarged view for describing the configuration of the turbine-side restraining portion shown inFIG. 4 . -
FIG. 7 is a sectional view for describing a disposition of a horizontal restraining portion and a vertical restraining portion shown inFIG. 2 . -
FIG. 8 is a partial enlarged view for describing a configuration of the horizontal restraining portion shown in FIG. 7. -
FIG. 9 is a sectional view for describing the configuration of the horizontal restraining portion shown inFIG. 7 taken along line A-A. -
FIG. 10 is a partial enlarged view for describing a configuration of the vertical restraining portion shown inFIG. 7 . -
- 1 gas turbine (rotary machine)
- 2A, 2B, 2C casing (support portion)
- 3 turbine portion (rotating portion)
- 5 inlet scroll portion (scroll structure)
- 6 discharge scroll portion (scroll structure)
- 21 scroll main body (casing)
- 22A turbine portion-side restraining portion (fitting portion)
- 22B casing-side restraining portion (fitting portion)
- 23A horizontal restraining portion (fitting portion)
- 23B vertical restraining portion (fitting portion)
- 31 annular channel
- 32 cylindrical channel
- 35 support portion
- 43A, 43B first protrusion
- 44A, 44B first groove
- 45A, 45B first depression
- 51A, 51B second protrusion
- 52A, 52B second depression
- A scroll structure according to an embodiment of the present invention and a gas turbine having the scroll structure will be described with reference to
FIGS. 1 to 10 . -
FIG. 1 is a schematic diagram for describing an entire configuration of the gas turbine according to the present embodiment. - A gas turbine (rotary machine) 1 includes casings (support portions) 2A, 2B and 2C constituting an outer shape of the
gas turbine 1, a turbine portion (rotating portion) 3 which extracts a rotational driving force from a supplied working fluid, a rotation shaft 4 which is rotated and driven around a rotational axis L by theturbine portion 3, an inlet scroll portion (scroll structure) 5 which supplies the working fluid to theturbine portion 3, and a discharge scroll portion (scroll structure) 6 into which the working fluid discharged from theturbine portion 3 flows. - As shown in
FIG. 1 , thecasings gas turbine 1 together with thecasing 2B. Theturbine portion 3, the rotation shaft 4, theinlet scroll portion 5 and thedischarge scroll portion 6 are accommodated in thecasings casings casings casings casing 2B interposed therebetween. - A through hole 7 is formed in the closed ends of the
casings opening 8 is formed in cylindrical surfaces of thecasings opening 8. - As shown in
FIG. 1 , thecasing 2B constitutes the outer shape of thegas turbine 1 together with thecasings turbine portion 3. - The
casing 2B is a substantially disk-like member extending in a radial direction centered on the rotational axis L, and is interposed between thecasings - As shown in
FIG. 1 , theturbine portion 3 includes arotor blade 11 and a stator blade 12 (seeFIG. 4 ). Theturbine portion 3 extracts a rotational driving force from the working fluid supplied from theinlet scroll portion 5, and rotates and drives the rotation shaft 4. - A known configuration can be used for the
turbine portion 3, and the configuration thereof is not especially limited. - The rotation shaft 4 is rotated and driven around the rotational axis L by the
turbine portion 3 as shown inFIG. 1 . - As shown in
FIG. 1 , the working fluid passes through theinlet scroll portion 5 and thedischarge scroll portion 6, and the working fluid is supplied to theturbine portion 3 as well as the working fluid discharged from theturbine portion 3 flows into theinlet scroll portion 5 and thedischarge scroll portion 6. Since the basic configurations of theinlet scroll portion 5 and thedischarge scroll portion 6 are substantially the same, only theinlet scroll portion 5 will be described below and description of the configuration of thedischarge scroll portion 6 is omitted. -
FIG. 2 is a perspective view for describing the configuration of the inlet scroll portion shown inFIG. 1 as viewed from the turbine portion.FIG. 3 is a perspective view for describing the configuration of the inlet scroll portion shown inFIG. 1 as viewed from the casing. - As shown in
FIGS. 2 and 3 , theinlet scroll portion 5 includes a scroll main body (casing) 21 constituting the outer shape of theinlet scroll portion 5, a turbine portion-side restraining portion (fitting portion) 22A, a casing-side restraining portion (fitting portion) 22B, a horizontal restraining portion (fitting portion) 23A, and a vertical restraining portion (fitting portion) 23B. These restraining portions support the scrollmain body 21 with respect to thecasing 2A such that the scroll can expand and contract along the radial direction centered on the rotational axis L, and restrain movement of the scrollmain body 21 in a direction along the rotational axis L. - As shown in
FIGS. 2 and 3 , the scrollmain body 21 is integrally formed into a ring shape provided at a central portion with an opening through which the rotation shaft 4 is inserted. As shown inFIG. 1 , the scrollmain body 21 is provided therein with anannular channel 31 extending annularly around the rotational axis L, and acylindrical channel 32 extending from theannular channel 31 toward the rotational axis L up to theturbine portion 3. -
FIG. 4 is a partial enlarged sectional view for describing configurations of the turbine portion-side restraining portion and the casing-side restraining portion shown inFIGS. 2 and 3 . As shown inFIG. 4 , the turbine portion-side restraining portion 22A is provided in the scrollmain body 21 on the side of theturbine portion 3. The turbine portion-side restraining portion 22A supports the scrollmain body 21 such that the scrollmain body 21 can expand and contract in the radial direction centered on the rotational axis L, and restrains movement of the scrollmain body 21 in the direction along the rotational axis L. The casing-side restraining portion 22B is provided in the scrollmain body 21 on the side of thecasing 2A. The casing-side restraining portion 22B supports the scrollmain body 21 such that the scrollmain body 21 can expand and contract in the radial direction centered on the rotational axis L and restrains movement of the scrollmain body 21 in the direction along the rotational axis L. - As shown in
FIG. 1 , theannular channel 31 has an annular shape into which the working fluid heated from outside flows. A cross sectional area of the channel is gradually reduced from a lower portion (lower portion inFIG. 1 ) to an upper portion along which the working fluid flows from outside. By forming theannular channel 31 in this shape, a flow velocity of the working fluid which flows into theturbine portion 3 is substantially equalized in the circumferential direction. - As shown in
FIGS. 1 and 4 , thecylindrical channel 32 extends from an inner periphery of theannular channel 31 toward the rotational axis L as well as extends toward theturbine portion 3. Thecylindrical channel 32 has such a shape that a pressure loss of the working fluid flowing through thecylindrical channel 32 is minimized. - In the
cylindrical channel 32 in theinlet scroll portion 5, the working fluid which flows into theturbine portion 3 from theannular channel 31 flows. In thecylindrical channel 32 in thedischarge scroll portion 6, the working fluid which flows into theannular channel 31 from theturbine portion 3 flows. -
FIGS. 5 and 6 are partial enlarged views for describing a configuration of the turbine-side restraining portion shown inFIG. 4 . - As shown in
FIGS. 4 and 5 , the turbine portion-side restraining portion 22A supports the scrollmain body 21 such that it can expand and contract in the radial direction, and restrains movement of the scrollmain body 21 in the direction along the rotational axis L. - The turbine portion-
side restraining portion 22A is provided with anouter ring 41A which is disposed on an inner peripheral surface of the scrollmain body 21, and with aninner ring 42A fixed to asupport portion 35 which is connected to thecasing 2A. - The
outer ring 41A is provided withfirst protrusions 43A which project radially inward and which are disposed at equal distances from one another in the circumferential direction. The distances of thefirst protrusions 43A correspond to the distances of later-describedfirst depressions 45A. - The
first protrusions 43A are fitted into later-describedfirst grooves 44A, thereby restraining movements of the scrollmain body 21 in the direction along the rotational axis L. - The
inner ring 42A is provided withfirst grooves 44A which are opened radially outward and extend in the circumferential direction, andfirst depressions 45A which are formed in awall portion 46A of a pair of wall portions located on the side of the scrollmain body 21, and which are depressed radially inward. The pair of wall portions constitute thefirst groove 44A. - The
first grooves 44A are fitted to thefirst protrusions 43A, restrain movement of the scrollmain body 21 in the direction along the rotational axis L, and permit movement of thefirst protrusions 43A in the circumferential direction. - When the
first protrusions 43A are fitted to or separated from thefirst grooves 44A, thefirst protrusions 43A move in the direction along the rotational axis L and pass through thefirst depressions 45A. Thefirst depressions 45A are provided as many as thefirst protrusions 43A at equal distances from one another in the circumferential direction. The distances between thefirst depressions 45A correspond to the distances between thefirst protrusions 43A. - In this configuration, the
first protrusions 43A can pass through thefirst depressions 45A and move in the direction along the rotational axis L. - The relative position between the
outer ring 41A and theinner ring 42A shown inFIG. 5 shows a positional relation in a case where thefirst protrusions 43A pass through thefirst depressions 45A. The relative position between theouter ring 41A and theinner ring 42A shown inFIG. 6 shows a positional relation in a case where thefirst protrusions 43A rotate in the circumferential direction and restrain movement of the scrollmain body 21 in the direction along the rotational axis L. - As shown in
FIG. 4 , the casing-side restraining portion 22B supports the scrollmain body 21 such that it can expand and contract in the radial direction and restrains movement of the scrollmain body 21 in the direction along the rotational axis L. - The casing-
side restraining portion 22B is provided with anouter ring 41B which is disposed on a surface of the scrollmain body 21 opposed to thecasing 2A, and with aninner ring 42B fixed to thesupport portion 35 which is connected to thecasing 2A. - Like the
outer ring 41A, theouter ring 41B is provided withfirst protrusions 43B which project radially inward and which are disposed at equal distances from one another in the circumferential direction. - Like the
inner ring 42A, theinner ring 42B is provided with afirst groove 44B which opens radially outward and which extends in the circumferential direction, and with afirst depression 45B which is depressed radially inward and which is formed in afirst wall portion 46B of a pair of wall portions constituting thefirst groove 44B on the side of the scrollmain body 21. -
FIG. 7 is a sectional view for describing positions of the horizontal restraining portion and the vertical restraining portion shown inFIG. 2 . - As shown in
FIG. 7 , thehorizontal restraining portion 23A and thevertical restraining portion 23B support the scrollmain body 21 such that it can expand and contract in the radial direction, and restrain movement of the scrollmain body 21 in the horizontal direction intersecting with the rotational axis L as well as in the vertical direction. - The
horizontal restraining portion 23A is disposed on an upper end (upper side end inFIG. 7 ) of the scrollmain body 21, and restrains movement of the scrollmain body 21 in the horizontal direction (lateral direction inFIG. 7 ) with respect to thecasing 2A. -
FIG. 8 is a partial enlarged view for describing a configuration of the horizontal restraining portion shown inFIG. 7 .FIG. 9 is a sectional view for describing the configuration of the horizontal restraining portion shown inFIG. 7 taken along the line A-A. - As shown in
FIGS. 8 and 9 , thehorizontal restraining portion 23A is provided with asecond protrusion 51A projecting radially inward from thecasing 2A, and apedestal 53A formed with asecond depression 52A which is opened radially outward. - As shown in
FIG. 8 , thesecond protrusion 51A includes abrim 61A which abuts against an outer peripheral surface of thecasing 2A, ashaft portion 62A which extends radially inward from thebrim 61A and which penetrates thecasing 2A, and an insertedportion 63A which configures a radially inner end of theshaft portion 62A and which is inserted into thesecond depression 52A. As shown inFIG. 9 , the insertedportion 63A has a rectangular cross section. - As shown in
FIG. 8 , thepedestal 53A is a rectangular parallelepiped member provided on the scrollmain body 21. Arib 64 extending radially outward and in the circumferential direction is provided on a side surface of thepedestal 53A. Thesecond depression 52A is provided on an upper surface of thepedestal 53A, i.e., the surface of thepedestal 53A opposed to thecasing 2A. - As shown in
FIG. 9 , thesecond depression 52A is a rectangular parallelepiped hole, and the insertedportion 63A is inserted into thesecond depression 52A. - As shown in
FIG. 7 , thevertical restraining portion 23B is disposed diagonally below the scrollmain body 21, e.g., at a phase rotated downward by about 20° from the horizontal direction, and thevertical restraining portion 23B restrains movement of the scrollmain body 21 in the vertical direction (vertical direction inFIG. 7 ) with respect to thecasing 2A. - The phase is not limited to 20° as long as movement in the vertical direction is restrained.
-
FIG. 10 is a partial enlarged view for describing the configuration of the vertical restraining portion shown inFIG. 7 . - As shown in
FIG. 10 , thevertical restraining portion 23B includes asecond protrusion 51B projecting radially inward from thecasing 2A, and apedestal 53B formed with asecond depression 52B which is opened radially outward. - Since the configurations of respective portions of the
vertical restraining portion 23B are the same as those of thehorizontal restraining portion 23A,FIG. 10 shows the configuration of thevertical restraining portion 23B and description thereof is omitted. - Next, operation of the
gas turbine 1 having the above-described configuration will be described. - As shown in
FIG. 1 , the working fluid which is heated to high temperature in a high temperature gas furnace flows into theinlet scroll portion 5 of thegas turbine 1. The working fluid which has flowed into theinlet scroll portion 5 flows into theannular channel 31, and then flows into thecylindrical channel 32 at a substantially even flow velocity in the circumferential direction. The working fluid which flowed into thecylindrical channel 32 is introduced into theturbine portion 3 and flows into theturbine portion 3. - As shown in
FIGS. 1 and 4 , therotor blade 11 is rotated and driven by the working fluid flowing in theturbine portion 3, and a rotational driving force extracted by therotor blade 11 is transmitted to the rotation shaft 4. The working fluid of which rotational driving force has been extracted by theturbine portion 3 and of which temperature has been lowered is discharged from theturbine portion 3. - As shown in
FIG. 1 , the working fluid discharged from theturbine portion 3 flows into thecylindrical channel 32 of thedischarge scroll portion 6 and flows toward theannular channel 31. The working fluid which has flowed into theannular channel 31 is discharged from thedischarge scroll portion 6, i.e., from thegas turbine 1, and is again introduced into the high temperature gas furnace through a device. - Next, a supporting method of the
inlet scroll portion 5 and thedischarge scroll portion 6 which are features of the present embodiment will be described. - First, support of the scroll
main body 21 by the turbine portion-side restraining portion 22A and the casing-side restraining portion 22B will be described with reference toFIGS. 4 to 6 . - When the scroll
main body 21 is supported by thesupport portion 35, as shown inFIGS. 4 and 6 , thefirst protrusions first grooves first protrusions wall portions - By disposing the
first protrusions main body 21 in the direction along the rotational axis L is restrained. By providing distances between inner peripheral ends of thefirst protrusions first grooves first protrusions first grooves - Next, a fitting method of the turbine portion-
side restraining portion 22A and the casing-side restraining portion 22B will be described. - First, the
inner ring 42A of the turbine portion-side restraining portion 22A is fixed to thesupport portion 35. Thereafter, the scrollmain body 21 is fitted to thesupport portion 35 through the turbine portion-side restraining portion 22A. - More specifically, the
first protrusion 43A and thefirst depression 45A are disposed at the relative positions shown inFIG. 5 , in other words, such that thefirst protrusion 43A is inserted through thefirst depression 45A and then, the scrollmain body 21 is moved toward theturbine portion 3 along the rotational axis L. - Once the
first protrusion 43A is moved into thefirst groove 44A, thefirst protrusion 43A is moved in the circumferential direction, and thefirst protrusion 43A is rotated to a location where it is overlapped with thewall portion 46A as viewed from the direction along the rotational axis L as shown inFIG. 6 . Accordingly, fitting operation of the turbine portion-side restraining portion 22A is completed. - By this operation, the rotation shaft 4 is inserted through the integrally formed scroll
main body 21 as well as the scrollmain body 21 is supported such that it can expand and contract along the radial direction. At the same time, movement of the scrollmain body 21 in the direction along the rotational axis L can be restrained. - More specifically, the
first protrusion 43A passes through thefirst depression 45A while moving thefirst protrusion 43A in the direction along the rotational axis L. Accordingly, thefirst protrusion 43A is disposed in thefirst groove 44A and the rotation shaft 4 penetrates the scrollmain body 21. Thereafter, thefirst protrusion 43A is rotated in the circumferential direction, and thefirst protrusion 43A is disposed in a region of thefirst groove 44A where thefirst depression 45A is not provided, in other words, in a region of thefirst groove 44A where the pair of wall portions are opposed to each other. Thus, movement of the scrollmain body 21 in the direction along the rotational axis L is restrained. - Next, the
inner ring 42B of the casing-side restraining portion 22B is fitted into theouter ring 41B. - More specifically, the
first protrusion 43B and thefirst depression 45B are disposed at the relative positions shown inFIG. 5 , and then theinner ring 42B is moved toward theturbine portion 3 along the rotational axis L. - Once the
first protrusion 43B is moved into thefirst groove 44B, theinner ring 42B is moved in the circumferential direction, and theinner ring 42B is rotated to a location where thefirst protrusion 43B and thewall portion 46B are overlapped with each other as viewed from the direction along the rotational axis L as shown inFIG. 6 . Accordingly, fitting operation of the casing-side restraining portion 22B is completed. - Next, support of the scroll
main body 21 by thehorizontal restraining portion 23A and thevertical restraining portion 23B will be described with reference toFIGS. 7 to 10 . - When the scroll
main body 21 is supported by thecasings FIGS. 7 , 8 and 10, thesecond protrusions casings second depressions main body 21. - As shown in
FIG. 8 , thesecond protrusion 51A of thehorizontal restraining portion 23A is inserted into thesecond depression 52A. Then, movement of the scrollmain body 21 in the horizontal direction is restrained. A gap is provided between an inner radial end of thesecond protrusion 51A and the bottom surface of thesecond depression 52A, so that expansion and contraction of the scrollmain body 21 in the radial direction are permitted. - By inserting the
second protrusion 51B of thevertical restraining portion 23B into thesecond depression 52B as shown inFIG. 10 , movement of the scrollmain body 21 in the vertical direction is restrained. On the other hand, when a gap is provided between an inner radial end of thesecond protrusion 51B and the bottom surface of thesecond depression 52B, expansion and contraction of the scrollmain body 21 in the radial direction are permitted. - According to the above-described configuration, by integrally forming the scroll
main body 21, leakage of the working fluid outside as well as inflow of other fluid caused by inhalation of the other fluid into the scrollmain body 21 from outside can be prevented. That is, when the scrollmain body 21 has such a configuration that it is divided into two pieces, i.e., the upper casing and the lower casing, there is an adverse possibility that a working fluid may leak from the joint surface between the upper casing and the lower casing. In the case of the integrally formed scrollmain body 21, since there is no joint surface, leakage of a working fluid can surely be prevented, and reliability of thegas turbine 1 can be improved. - By integrally forming the scroll
main body 21, as compared with a case where the scrollmain body 21 is divided into two pieces, thecylindrical channel 32 can be formed into such a shape that a pressure loss thereof is suppressed. That is, when the scrollmain body 21 is divided into two pieces, since a space for disposing a member such as a bolt which fastens the upper casing and the lower casing to each other and an space for operating attachment or detachment of the bolt must be secured, the shape of thecylindrical channel 32 is limited. To the contrary, in the case where the scrollmain body 21 is integrally formed in one piece, it is unnecessary to use the fastening bolt, the shape of the channel is not limited, and thus the channel shape causing a small pressure loss can be employed. Therefore, performance of thegas turbine 1 can be improved. - By integrally forming the scroll
main body 21, as compared with the case where the scrollmain body 21 is divided into two pieces, the scroll structure can be reduced in size. Specifically, when the scrollmain body 21 is divided into two pieces, the flanges used for fastening the upper casing and the lower casing to each other project outward from the casings. To the contrary, in the case of the integrally formed scrollmain body 21, since it is unnecessary to provide the flanges, the scrollmain body 21 can be made smaller, and thegas turbine 1 can be reduced in size. - The scroll
main body 21 is supported by the turbine portion-side restraining portion 22A, the casing-side restraining portion 22B, thehorizontal restraining portion 23A and thevertical restraining portion 23B such that the scrollmain body 21 can expand and contract in the radial direction. Therefore, it is possible to prevent misalignment of the scrollmain body 21 which may be caused in a case where deformation of the scrollmain body 21 is restrained, and damage to the scrollmain body 21 caused by high stress. - For example, in a case where even a single fixed point is provided to the scroll
main body 21, misalignment of the scrollmain body 21 may be caused by uneven deformation. In the case where the fixed point is provided, there is an adverse possibility that thermal deformation of the scrollmain body 21 is restrained and thermal stress is caused, and thus the scrollmain body 21 is damaged. - When the scroll
main body 21 is supported such that the scrollmain body 21 can expand and contract along the radial direction, thermal deformation of the scrollmain body 21 is not restrained, misalignment and thermal stress of the scrollmain body 21 can be suppressed, and therefore reliability of thegas turbine 1 can be improved. - The technical scope of the present invention is not limited to the above embodiment, and the present invention can variously be modified within a range not departing from the subject matter of the present invention.
- For example, although the present invention is applied to the axial-flow turbine in the above embodiment, the present invention is not limited to such an axial-flow turbine, but can also be applied to other kinds of turbines such as a centrifugal type turbine and a mixed-flow turbine.
- The present invention can also be applied to general fluid machines such as a gas turbine of another type in which air is employed as a working fluid and combustion energy of fossil fuel or the like is used as a heat source, as well as a steam turbine, a compressor, and a pump. Applications of the present invention are not especially limited.
Claims (4)
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JP2008093734 | 2008-03-31 | ||
JP2008-093734 | 2008-03-31 | ||
PCT/JP2009/056927 WO2009123300A2 (en) | 2008-03-31 | 2009-03-27 | Rotary machine scroll structure and rotary machine |
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US20100296923A1 true US20100296923A1 (en) | 2010-11-25 |
US8757964B2 US8757964B2 (en) | 2014-06-24 |
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US12/747,978 Active 2031-07-31 US8757964B2 (en) | 2008-03-31 | 2009-03-27 | Rotary machine scroll structure and rotary machine |
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US (1) | US8757964B2 (en) |
EP (1) | EP2304192B1 (en) |
JP (1) | JP5073060B2 (en) |
CN (1) | CN101952556B (en) |
RU (1) | RU2470161C2 (en) |
WO (1) | WO2009123300A2 (en) |
ZA (1) | ZA201004495B (en) |
Cited By (4)
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US20150267565A1 (en) * | 2012-10-22 | 2015-09-24 | Nuovo Pignone Srl | Exhaust gas collector and gas turbine |
RU191521U1 (en) * | 2019-03-04 | 2019-08-12 | Публичное Акционерное Общество "Одк-Сатурн" | GAS REDUCTION ASSEMBLY FOR A GAS TURBINE ENGINE |
WO2020040720A1 (en) * | 2018-08-20 | 2020-02-27 | Siemens Aktiengesellschaft | Assembly and method for supporting turbine exhaust diffuser |
US11286810B2 (en) | 2016-08-23 | 2022-03-29 | Siemens Energy Global GmbH & Co. KG | Outflow housing of a steam turbine |
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US10094288B2 (en) * | 2012-07-24 | 2018-10-09 | Icr Turbine Engine Corporation | Ceramic-to-metal turbine volute attachment for a gas turbine engine |
WO2014130217A1 (en) * | 2013-02-22 | 2014-08-28 | United Technologies Corporation | Gas turbine engine attachment structure and method therefor |
CN106968984B (en) * | 2015-12-11 | 2020-10-23 | 松下知识产权经营株式会社 | Turbine engine |
RU2678793C1 (en) * | 2018-03-05 | 2019-02-05 | Публичное акционерное общество "ОДК - Уфимское моторостроительное производственное объединение" (ПАО "ОДК-УМПО") | Gas compressor unit, gas turbine plant (gtp), input device of gtp gas compressor unit (options), support complex of the input device gtp gas compressor unit |
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- 2009-03-27 WO PCT/JP2009/056927 patent/WO2009123300A2/en active Application Filing
- 2009-03-27 JP JP2010524011A patent/JP5073060B2/en not_active Expired - Fee Related
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US20050053463A1 (en) * | 2003-03-19 | 2005-03-10 | Abb Turbo Systems Ag | Exhaust-gas-turbine casing |
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US20150267565A1 (en) * | 2012-10-22 | 2015-09-24 | Nuovo Pignone Srl | Exhaust gas collector and gas turbine |
US11286810B2 (en) | 2016-08-23 | 2022-03-29 | Siemens Energy Global GmbH & Co. KG | Outflow housing of a steam turbine |
WO2020040720A1 (en) * | 2018-08-20 | 2020-02-27 | Siemens Aktiengesellschaft | Assembly and method for supporting turbine exhaust diffuser |
RU191521U1 (en) * | 2019-03-04 | 2019-08-12 | Публичное Акционерное Общество "Одк-Сатурн" | GAS REDUCTION ASSEMBLY FOR A GAS TURBINE ENGINE |
Also Published As
Publication number | Publication date |
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RU2010125706A (en) | 2012-05-10 |
CN101952556B (en) | 2015-03-04 |
JP5073060B2 (en) | 2012-11-14 |
WO2009123300A3 (en) | 2010-09-30 |
CN101952556A (en) | 2011-01-19 |
WO2009123300A2 (en) | 2009-10-08 |
US8757964B2 (en) | 2014-06-24 |
ZA201004495B (en) | 2013-03-27 |
EP2304192A2 (en) | 2011-04-06 |
EP2304192B1 (en) | 2014-12-10 |
JP2011506810A (en) | 2011-03-03 |
RU2470161C2 (en) | 2012-12-20 |
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